WO2011033721A1

WO2011033721A1 - Drive device

Info

Publication number: WO2011033721A1
Application number: PCT/JP2010/005106
Authority: WO
Inventors: 貢山下; 昭次高橋; 美紗紀神谷; 雅之内田
Original assignee: アイシン・エィ・ダブリュ株式会社
Priority date: 2009-09-18
Filing date: 2010-08-18
Publication date: 2011-03-24
Also published as: JP2011085255A; DE112010000425T5; US20110070990A1; CN102378867A

Abstract

Provided is a structure wherein a partition is used to separate a traction oil space from a lubricating oil space for the purpose of disposing a cone ring type infinite variable-speed drive in the traction oil space and wherein a friction wheel is supported on the partition via a bearing. The shaft section (22b) of an input side friction wheel is supported by a tapered roller bearing (27) installed on the partition. A sleeve (60) is press-fitted into an inner race (27a). The inside diameter portion of the sleeve (60) has a large diameter socket section (60b), a small diameter socket section (60d), and a splined section (60c). The shaft section (22b) is fitted into the aforementioned two socket sections (60b, 60d) with some play allowed, and engages the splined section (60c) in such a way as to be splined together. Furthermore, the bearing is installed by being held between a nut (32) and a stepped section (a).

Description

Drive device

The present invention relates to a drive device provided with a friction-type continuously variable transmission such as a cone ring type and a gear transmission constituted by meshing rotation transmission means (gear, chain, sprocket, etc.).

Conventionally, a drive device, for example, a hybrid drive device, in which a continuously variable transmission and a gear transmission are integrated is known. In general, a continuously variable transmission for the hybrid drive device is composed of a pair of pulleys and a metal belt (or chain) wound around the pulleys, and the belt continuously variable by changing the effective diameter of the pulleys. A continuously variable transmission is used.

On the other hand, it is composed of a pair of conical friction wheels and a metal ring interposed between these friction wheels. By moving the ring so as to change the contact portion with the two friction wheels, it is continuously variable. 2. Description of the Related Art A cone-ring friction continuously variable transmission that changes speed is known (see, for example, Patent Document 1).

JP 2006-501425 A (JP 2006-501425A)

In a conventional drive device, a belt-type continuously variable transmission and a gear transmission composed of a plurality of gears are housed in the same case and are lubricated by the same lubricating oil such as ATF.

It is also conceivable that the cone ring type continuously variable transmission is applied to a continuously variable transmission for the driving device. In this case, in the belt type continuously variable transmission, a desired transmission torque can be obtained even if lubricating oil is interposed, but a cone ring type consisting of a frictional contact between a conical friction wheel and a metal ring. In the friction type continuously variable transmission, it is difficult to obtain a desired transmission torque with the lubricating oil, and it is preferable to interpose a dedicated traction oil that can obtain a sufficient shear torque.

For this reason, the drive device to which the friction type continuously variable transmission is applied includes a first space that houses the friction type continuously variable transmission, and a second space that houses a gear transmission composed of rotation transmission means by meshing. It is preferable that the partition wall is oil-tightly partitioned, the traction oil is filled in the first space, and the lubricating oil is filled in the second space.

Since the cone ring type friction continuously variable transmission applies a large contact pressure between the ring and the two friction wheels, it is necessary to apply a large thrust force (axial force) to the friction wheel. Generally, in the friction type continuously variable transmission, a bearing inner race is press-fitted into the shafts of both friction wheels and supported by a case. However, when the partition wall is used, the conical friction wheel is attached to the friction wheel with the shaft portion on one side supported by the case, and the partition wall is assembled in this state, and the bearing is assembled to the partition wall. It is an assembly procedure for supporting the shaft portion on the side, but it is preferable to arrange a bearing that receives a thrust force on the second space side, so that one side of the friction wheel is supported on the case, and the other side It is difficult to assemble the bearing with the inner race while the inner race of the bearing is press-fitted into both shaft portions.

That is, it is difficult in terms of accuracy to insert both the friction wheels on the input side and the output side into the bearings having both other end side shaft portions mounted on the partition walls.

Therefore, an object of the present invention is to provide a drive device in which the shaft portion of a conical friction wheel on which a thrust force acts is supported by a partition wall on the second space side, thereby eliminating the above-described problems.

The present invention comprises a first space (A) that houses a friction type continuously variable transmission (3) and is filled with traction oil, and rotation transmission means (16, 17, 19, 41, 44) by meshing. Drive unit (7), in which a case (11) is oil-tightly partitioned by a partition wall (12) in a second space (B) in which a gear transmission (7) to be stored is housed and filled with lubricating oil. In 1)
The friction-type continuously variable transmission is arranged such that an input member (22) formed of a conical friction wheel and a large-diameter portion and a small-diameter portion are parallel to the input member and have a large-diameter portion and a small-diameter portion reversed in the axial direction. An output member (23) formed of a conical friction wheel and a ring (25) sandwiched between inclined surfaces facing each other of the friction wheels, and the ring is moved in the axial direction for continuously variable transmission. A corn ring type continuously variable transmission (3),
One of the input member (22) and the output member (23) has a shaft portion (22a) on one side rotatably supported by the case (11) and a shaft portion (22b) on the other side. Is supported on the second space (B) side of the partition wall (12) via a bearing (27) that supports a thrust direction and a radial direction,
The bearing (27) is mounted on the partition wall (12), and the inner race (27a, 27a2, 27a3) is connected to the other shaft portion ( 22b) is connected non-rotatably,
In the drive device characterized by this.

In the present invention, the gear includes gears (toothed gears) and sprockets (sprockets), and means a rotation transmission means by meshing. Therefore, the gear transmission is transmitted by the meshing rotation transmission means. Means device.

Preferably, the one member is an input member, the shaft portion on one side of the input member is on the large diameter side of the friction wheel, and the shaft portion on the other side is small in diameter of the friction wheel. It is the club side.

For example, referring to FIG. 3, a sleeve (60) is press-fitted into the inner race (27a), and the sleeve (60) has a large-diameter inlay part (60b), a small-diameter inlay part (60d), and the It has a spline part (60c) between both spigot parts,
The shaft portion (22b) on the other side is supported (b, d) by loose fitting on both the spigot portions and is spline engaged (c) with the spline portion (60c).

For example, referring to FIG. 4, the inner race (27a2) has a large-diameter spigot part (70b), a small-diameter spigot part (70d) on its inner diameter side, and a spline part (70c) between the two spigot parts. ,
The shaft portion (22b) on the other side is supported by loose fitting (b, d) on both the spigot portions and is spline engaged (c) with the spline portion (70c).

For example, referring to FIG. 5, a stepped portion (a) is provided on the shaft portion (22b) on the other side, and a protrusion (81) or a notch is provided on the stepped portion.
The inner race (27a3) is provided with a notch (80a) or a protrusion on one end face thereof, and the other side shaft (22b) is supported by the inner race (27a3) by loose fitting (h). At the same time, the protrusion (81) is engaged with the notch (80a) so as not to rotate.

For example, referring to FIGS. 3 to 5, the shaft portion (22b) on the other side has a stepped portion (a) and a male screw portion (e) at the tip portion.
The inner race (27a, 27a2, 27a3) is tightened with a nut (32) screwed into the male screw portion (e) between the stepped portion (a) and the inner race (27a, 27a2, 27a3). ) Is integrally attached to the shaft portion (22b) on the other side in the axial direction.

The bearing is a tapered roller bearing (27) that supports a thrust force toward the large diameter portion of the input member (22).

The case (11) has a first case member (9) and a second case member (10) coupled to each other,
As for the said input member (22), the said axial part (22a) is supported by the said 1st case member (9) via the radial bearing (26),
The output member (23) has a shaft portion (23a) on one side supported by the first case member (9) via a radial bearing (29) and a shaft portion (23b) on the other side being a radial bearing. Supported by the partition wall (12) via (30),
Between the output member (23) and the continuously variable transmission output shaft (24), an axial force applying means for applying an axial force corresponding to the output torque is interposed,
The continuously variable transmission output shaft (24) is tapered on the second space (B) side of the second case member (10) to support the thrust force in the reaction force direction of the axial force applying means. It is supported via a roller bearing (31).

An input shaft (6) linked to the engine;
An electric motor (2) having a dedicated output shaft (4);
A differential device (5),
The friction type continuously variable transmission (3) shifts the rotation of the input shaft (6) continuously and outputs it to the continuously variable transmission output shaft (24),
The gear transmission (7) is configured to transmit the rotation of the output shaft (4) of the electric motor (2) to the differential device (5) via the continuously variable transmission output shaft (24).

In addition, although the code | symbol in the said parenthesis is for contrast with drawing, it does not have any influence on the structure as described in a claim by this.

According to the first aspect of the present invention, at least one member of the shaft portion on the partition wall side of the pair of conical friction wheels is supported by the inner race of the bearing with a margin for rotation prevention. This friction wheel can be supported by mounting its shaft portion on the partition wall via a bearing.

Further, the cone ring type continuously variable transmission is housed in the first space filled with the traction oil, and the continuously variable transmission has a shearing force, particularly a traction oil having a large shearing force in an extreme pressure state. A large thrust force acting on one member of the continuously variable transmission while transmitting a torque through an oil film, transmitting a desired torque reliably over a long period of time, and enabling a quick and smooth speed change. Is supported by a bearing disposed on the second space side of the partition wall, so that the bearing is lubricated by the lubricating oil filled in the second space and maintains high shaft support accuracy over a long period of time. can do.

According to the second aspect of the present invention, when the one member is an input member, a large thrust force acts on the partition wall side, but the shaft portion on the other side, which is the small diameter side of the input member, has the thrust. It is supported by the partition wall through bearings that support the direction and the radial direction.

According to the third or fourth aspect of the present invention, the sleeve or the inner race has the large-diameter and small-diameter inlay portions at both end portions, the spline portion between the two portions, and the other side portion of the input member as the both inlay portions. Since the shaft portion on the other side of the input member can be inserted into the partition wall with a margin by loose fitting (gap fitting) and is supported by The inner race rotates integrally with the shaft portion by spline engagement, and the other side shaft portion is supported by the partition wall so that the continuously variable transmission can be assembled. Further, the shaft portion is fitted and supported at both end portions and is spline-engaged between the two portions so as to be appropriately supported by the bearing.

According to the third aspect of the present invention, since the sleeve is press-fitted into the inner race and the large-diameter and small-diameter inlay portions and the spline portion are formed in the sleeve, the inner race may be a normal bearing inner race. No need for bearings.

According to the fifth aspect of the present invention, the inner race can be prevented from rotating with a simple structure in which a notch or a protrusion is formed in the inner race.

According to the sixth aspect of the present invention, since the inner race of the bearing is sandwiched between the stepped portion of the shaft portion and the nut and attached integrally in the axial direction, the thrust force acting on the input member is It can be reliably supported by the partition via the bearing.

According to the seventh aspect of the present invention, the thrust force in one direction acting on the input member can be reliably supported by the tapered roller bearing along with the radial direction.

According to the eighth aspect of the present invention, the continuously variable transmission is applied with an axial force corresponding to the output torque by the axial force applying means interposed between the output member and the output shaft, and is increased by an appropriate contact pressure. Torque can be reliably transmitted without causing power loss, and the thrust force due to the axial force is supported by being canceled together in the case, and does not require an external force for carrying the axial force.

According to the ninth aspect of the present invention, the differential device is applied to a hybrid drive device to transmit the power of the electric motor to the differential device with high efficiency and to change the rotation of the engine quickly and smoothly continuously. With a relatively inexpensive configuration by using a friction-type continuously variable transmission with a simple configuration, controlling the engine quickly and appropriately while assisting the electric motor appropriately Thus, it is possible to provide a hybrid drive device capable of sufficiently improving fuel consumption and reducing CO ₂ .

The front sectional view showing the hybrid drive device to which the present invention is applied. The side view. The expanded front sectional view which shows the support part of the axial part by the side of the partition of an input member. Sectional drawing by other embodiment which shows support of the said axial part. 4A and 4B are views showing support of a shaft portion according to a further modified embodiment, where FIG. 5A is a cross-sectional view of an inner race, and FIG. 5B is a cross-sectional view taken along line BB in FIG.

A hybrid drive device to which the present invention is applied will be described with reference to the drawings. As shown in FIGS. 1 and 2, the hybrid drive device 1 includes an electric motor 2, a cone ring type continuously variable transmission (friction type continuously variable transmission) 3, a differential device 5, and an output shaft of an engine (not shown). And an input shaft 6 interlocking with the gear transmission 7. Each of the above devices and shafts is housed in a case 11 configured by combining two

case members

9 and 10, and the case 11 is divided into a first space A and a second space B by a partition wall 12. It is partitioned in an oil-tight manner.

The electric motor 2 has a stator 2 a fixed to the first case member 9 and a rotor 2 b provided on the output shaft 4, and the output shaft 4 has a bearing on the first case member 9 at one end. 13, and the other end is rotatably supported by the second case member 10 via a bearing 15. An output gear 16 composed of a gear (pinion) is formed on one side of the output shaft 4, and the output gear 16 meshes with an intermediate gear (gear) 19 provided on the input shaft 6 via an idler gear 17. ing.

One end of the shaft 17 a of the idler gear 17 is rotatably supported by the partition wall 12 via a bearing 20, and the other end is rotatably supported by the second case member 10 via a bearing 21. ing. The idler gear 17 is arranged in a state of being partially overlapped with the electric motor 2 in a side view (when viewed from the axial direction).

The cone ring type continuously variable transmission 3 includes a conical friction wheel 22 that is an input member, a conical friction wheel 23 that is an output member, and a metal ring 25. The

friction wheels

22 and 23 are arranged so that the large diameter portion and the small diameter portion are opposite to each other in the axial direction in parallel to each other, and the ring 25 is inclined so that the

friction wheels

22 and 23 face each other. It is arranged so as to be sandwiched between the surfaces and to surround one of the two friction wheels, for example, the input side friction wheel 22. A large thrust force acts on at least one of the two friction wheels, and the ring 25 is clamped by a relatively large clamping pressure based on the thrust force. Specifically, an axial force applying means (not shown) made of a cam mechanism is formed between the output-side friction wheel 23 and the continuously variable transmission output shaft 24 on the axially opposed surface. A thrust force in the direction of arrow D corresponding to the transmission torque is generated in the side friction wheel 23, and a large pinching pressure is generated in the ring 25 with the input side friction wheel 22 supported in a direction opposed to the thrust force. .

One end (large diameter portion) of the input side friction wheel 22 is supported by the first case member 9 via a roller bearing 26, and the other side (small diameter portion) end is a tapered roller bearing. 27 and supported by the partition wall 12. One end (small diameter portion) of the output side friction wheel 23 is supported by the first case member 9 via a roller (radial) bearing 29, and the other side (large diameter portion) end portion of the output side friction wheel 23 is supported. It is supported by the partition wall 12 via a roller (radial) bearing 30. The output shaft 24 in which the thrust force in the direction of arrow D described above is applied to the output side friction wheel 23 is supported by the second case member 10 via the tapered roller bearing 31 at the other side end. The other end portion of the input side friction wheel 22 has an inner race of a bearing 27 sandwiched between a stepped portion and a nut 32, and from the output side friction wheel 23 acting on the input side friction wheel 22 via a ring 25. The thrust force in the direction of arrow D is carried by the tapered roller bearing 27. On the other hand, the reaction force of the thrust force acting on the output side friction wheel 23 acts on the output shaft 24 in the counter arrow D direction, and the thrust reaction force is carried by the tapered roller bearing 31.

The ring 25 is moved in the axial direction by an axial movement means such as a ball screw to change the contact position between the input side friction wheel 22 and the output side friction wheel 23, and between the input member 22 and the output member 23. The speed ratio is continuously variable. The thrust force D corresponding to the transmission torque is canceled out in the integrated case 11 via the tapered

roller bearings

27 and 31 and does not require an equilibrium force as an external force such as hydraulic pressure.

The differential device 5 has a differential case 33. One end of the differential case 33 is supported by the first case member 9 via a bearing 35, and the other end is a second case member. 10 through a bearing 36. A shaft orthogonal to the axial direction is mounted inside the differential case 33,

bevel gears

37 and 37 serving as differential carriers are engaged with the shaft, and left and right axle shafts 39l and 39r are supported. Bevel gears 40 and 40 that mesh with the differential carrier are fixed to the shaft. Further, a large-diameter differential ring gear (gear) 41 is attached to the outside of the differential case 33.

A gear (pinion) 44 is formed on the continuously variable transmission output shaft 24, and the gear 44 is engaged with the diff ring gear 41. The motor output gear (pinion) 16, idler gear 17 and intermediate gear (gear) 19, continuously variable transmission output gear (pinion) 44 and diff ring gear (gear) 41 constitute the gear transmission 5. The motor output gear 16 and the diff ring gear 41 are arranged so as to overlap in the axial direction, and the intermediate gear 19 and the continuously variable transmission output gear 44 are further in the axial direction with the motor output gear 16 and the diff ring gear. They are arranged to overlap. The gear 45 that is spline-engaged with the continuously variable transmission output shaft 24 is a parking gear that locks the output shaft at the parking position of the shift lever. Further, the gear means a meshing rotation transmission means including a gear and a sprocket. In the present embodiment, the gear transmission means a gear transmission consisting of all gears.

The input shaft 6 is supported by the second case member 10 by a roller bearing 48, and is engaged (drive coupled) to the input member 22 of the continuously variable transmission 3 by a spline S at one end thereof, and The other end side is linked to the output shaft of the engine via a clutch (not shown) housed in a third space C formed by the second case member 10. The third space C side of the second case member 10 is open and connected to an engine (not shown).

The gear transmission 7 is accommodated in the electric motor 2 and a second space B which is a portion between the first space A and the third space C in the axial direction, and the second space B is The second case member 10 and the partition wall 12 are formed. The shaft support portions (27, 30) of the partition wall 12 are oil-tightly partitioned by oil seals 47, 49, and the shaft support portions of the second case member 10 and the first case member 9 are also oil seals. The second space B is sealed with a

shaft

50, 51, 52, and is configured to be oil-tight, and the second space B is filled with a predetermined amount of lubricating oil such as ATF. The first space A formed by the first case member 9 and the partition wall 12 is similarly configured to be oil-tight, and the first space A has a shearing force, particularly a shearing force in an extreme pressure state. Is filled with a predetermined amount of large traction oil.

Referring to FIG. 2, the output shaft 4 of the electric motor 2 is a first shaft I, the input shaft 6 and the continuously variable transmission input member 22 arranged coaxially are the second shaft II, and the continuously variable The transmission output member 23 and its output shaft 24 are the third axis III, the left and

right axle shafts

391 and 39r are the fourth axis IV, and the idler gear shaft 17a is the fifth axis V. These axes are all parallel to each other. Arranged and supported by the case 11, gears (gears) 16, 17, 19, 44, 41 of the gear transmission 7 are arranged. With respect to the gear transmission 7, the electric motor 2 and the continuously variable transmission 3 are arranged in one axial direction, and the engine is connected to the other. Further, the first axis I coaxial with the electric motor 2 is positioned at the uppermost position, and the fourth axis IV coaxial with the differential apparatus 5 is positioned at the lowest position, and a part of the ring gear 41 of the differential apparatus 5 is part of the above-mentioned. It is immersed in an oil reservoir of lubricating oil in the second space B.

Next, the operation of the hybrid drive device 1 described above will be described. The hybrid drive device 1 is used in such a manner that the third space C side of the case 11 is coupled to an internal combustion engine, and the output shaft of the engine is linked to the input shaft 6 via a clutch. The rotation of the input shaft 6 to which power from the engine is transmitted is transmitted to the input side friction wheel 22 of the cone ring type continuously variable transmission 3 via the spline S, and further to the output side friction wheel 23 via the ring 25. Communicated.

At this time, a large contact pressure acts between the

friction wheels

22, 23 and the ring 25 due to the thrust force in the direction of arrow D acting on the output-side friction wheel 23, and the traction oil is in the first space A. Since it is filled, an extreme pressure state in which an oil film of the traction oil is interposed between the two friction wheels and the ring. In this state, since the traction oil has a large shearing force, power is transmitted between the friction wheels and the ring by the shearing force of the oil film. Accordingly, the friction wheel and the ring can be transmitted without slipping while being in contact with each other, and the predetermined torque can be transmitted without slipping, and the ring 25 can be smoothly moved in the axial direction. The contact position is changed to change continuously.

The rotation of the continuously variable speed output side friction wheel 23 is transmitted to the differential case 33 of the differential device 5 through the output shaft 24, the output gear 44 and the differential ring gear 41, and power is distributed to the left and right axle shafts 39l and 39r. Then, the wheel (front wheel) is driven.

On the other hand, the power of the electric motor 2 is transmitted to the input shaft 6 via the output gear 16, the idler gear 17 and the intermediate gear 19. The rotation of the input shaft 6 is continuously variable via the cone ring type continuously variable transmission 3 and further transmitted to the differential device 5 via the output gear 44 and the diff ring gear 41 as described above. . The gear transmission 7 comprising the

gears

16, 17, 19, 44, 41, 37, 40 is housed in the second space B filled with lubricating oil, and the lubricating oil is engaged when the gears are engaged. Smoothly transmits power. At this time, the differential ring gear 41 (see FIG. 2) disposed at a position below the second space B scoops up the lubricating oil in combination with the large-diameter gear, and other gears (gears). 16, 17, 19, 44 and the

bearings

27, 30, 20, 21, 31, 48 are reliably and sufficiently supplied with lubricating oil.

The operation modes of the engine and the electric motor, that is, the operation modes of the hybrid drive device 1 can be variously adopted as necessary. As an example, when the vehicle starts, the clutch is disengaged and the engine is stopped, the engine is started only by the torque of the electric motor 2, and when the vehicle reaches a predetermined speed, the engine is started and accelerated by the power of the engine and the electric motor. Then, the electric motor is set to the free rotation or regenerative mode and travels only by the engine. During deceleration and braking, the electric motor is regenerated to charge the battery. Alternatively, the clutch may be used as a starting clutch, and may be used to start while using the motor torque as an assist by the power of the engine.

Next, the shaft support of the conical friction wheel 22 as an input member will be described. Both the

friction wheels

22 and 23 of the input member and the output member are assembled with the first case member 9 facing down and the axial direction being the vertical direction. That is, first, the outer race is press-fitted into the first case member 9 and both

roller bearings

26 and 29 are attached to the first case member 9, and the

inner shaft portions

22 a and 23 a (see FIG. 1) are inserted into the inner side. The two

friction wheels

22 and 23 are assembled to the first case member 9 with the race being press-fitted. In this state, the ring 25 is inserted between the

friction wheels

22 and 23 so as to surround the input side friction wheel 22, and the partition wall 12 with the oil seals 47 and 49 and the

bearings

27 and 30 attached thereto is assembled. Further, between the other side shaft portion 23b of the output side friction wheel 23 and the partition wall 12, a roller bearing 30 is mounted by press-fitting / removing the outer race into the partition wall and press-fitting / removing the inner race into the shaft portion. Is done.

The tapered roller bearing 27 that supports the other side shaft portion 22b of the input side friction wheel 22 is mounted on the partition wall 12 together with the roller and the inner race when the outer race is press-fitted into the partition wall 12. At this time, as shown in detail in FIG. 3, a sleeve 60 is press-fitted into the inner diameter side of the inner race 27 a and fixed integrally. The sleeve 60 has a flange portion 60a whose one end side (conical shape side) expands in the outer diameter direction, and the inner diameter side has a large diameter inlay portion 60b and a spline from the conical shape side toward the distal end side. A portion 60c and a small diameter inlay portion 60d are sequentially formed.

On the other hand, the other side shaft portion 22b of the input side friction wheel 22 has a stepped portion a, a large-diameter support portion b, a spline portion c, a small-diameter support portion d, and a male screw portion e from the conical shape side toward the tip. It is formed sequentially. The partition wall 12 is assembled so that the other side shaft portion 22b is inserted into the sleeve 60 press-fitted into the bearing 27 integrally. At this time, the large diameter inlay portion 60b of the sleeve 60 and the large diameter support portion b of the shaft portion 22b are fitted in a loose fit state, and the small diameter inlay portion 60d and the small diameter support portion d are in a loose fit state. The two

spline portions

60c and 60c are engaged with each other. As a result, even when the inner race is pressed into the other side shaft portion 23b of the output side friction wheel 23 and is supported by the roller bearing 30, the other side shaft portion 22b of the input side friction wheel 22 is loosely fitted. The partition wall 12 can be inserted by accommodation. Further, the nut 32 is screwed into the male screw portion e, the flange portion 60a of the sleeve 60 is brought into contact with the stepped portion a, and the nut 32 is pressed against the outer side surface of the inner race 27a. 27 is tightened so as to be restricted from moving in the axial direction. At this time, a gap g is formed between the nut 32 and the tip portion of the sleeve 60.

In this state, the other-side shaft portion 22b of the input-side friction wheel 22 is fitted and supported by the sleeve 60 integral with the bearing 27 at the inlay portions at both axial end portions, and between the axial direction portions. The sleeve 60 and the inner race 27a are sandwiched between the stepped portion a and the nut 32, and are supported integrally in the axial direction. Accordingly, the two

friction wheels

22 and 23 are supported by the first case member 9 with the

bearings

26 and 29 on the one

side shaft portions

22a and 23a, and the other

side shaft portions

22b and 23b on the

bearing

27, 30 is supported by the partition wall 12.

The input side friction wheel 22 is fitted and supported by the sleeve 60 press-fitted into the tapered roller bearing 27 in the rotation direction and the axial direction integrally with both the spigot part and the support part, and reliably carries a large thrust force in the direction of arrow D. Supported by At this time, the partition wall 12 is inserted into both the

shaft portions

22b and 23b and easily assembled based on the loose fitting state of the both spigot portions and the support portion. Further, since both the

bearings

27 and 30, particularly the tapered roller bearing 27 on which a large thrust force acts, are arranged in the second space B filled with the lubricating oil, the lubricating oil is lubricated for a long period of time. High shaft support accuracy can be maintained. Further, even if the other side shaft portion 22b of the input side friction wheel 22 is supported by the bearing 27 by loose fitting, a large axial force D acts on the output side friction wheel 23 by the axial force applying means. A large contact pressure with respect to 25 is always maintained, and a radial force in a direction away from the output side friction wheel 23 based on the thrust force always acts, so that the both inlay

portions

60b and 60d and the support portions b and d are in the radial direction. The shaft accuracy of the other side shaft portion 22b of the input side friction wheel (the accuracy between the shafts with the output side friction wheel) is maintained.

In the state where the partition wall 12 is assembled, the input shaft 6 is spline-engaged (S) with the shaft portion 22b of the input side friction wheel 22, and the electric motor 2, the idler gear 17, the continuously variable transmission output shaft 24. The second case member 10 is assembled by mounting the differential device 5 between the partition wall 12 and the differential case 5.

Next, another embodiment relating to the support of the other side shaft portion 22b of the input side friction wheel 22 will be described.

FIG. 4 is a view showing an embodiment in which the inner race 27a2 of the tapered roller bearing 27 is directly supported on the shaft portion 22b without using the sleeve described above.

Inside the inner race 27a2, a large-diameter spigot portion 70b, a spline portion 70c, and a small-diameter spigot portion 70d are sequentially formed from one end side (conical shape side) to the tip end side.

On the other hand, the other side shaft portion 22b of the input side friction wheel 22 has a stepped portion a, a large diameter support portion b, a spline portion c, a small diameter support portion d, Male threaded portions e are sequentially formed. The partition wall 12 is assembled so that the other side shaft portion 22b is inserted into the inner race 27a2 of the bearing 27. At this time, the large-diameter inlay portion 70b of the inner race 27a2 and the large-diameter support portion b of the shaft portion 22b are fitted in a loose fit state, and the small-diameter inlay portion 70d and the small-diameter support portion d are loosely fitted. And both the spline portions 70c, c are engaged. As a result, even when the inner race is pressed into the other side shaft portion 23b of the output side friction wheel 23 and is supported by the roller bearing 30, the other side shaft portion 22b of the input side friction wheel 22 is loosely fitted. The partition wall 12 can be inserted by accommodation. Further, the nut 32 is screwed into the male thread portion e, the one end surface of the inner race 27a2 is brought into contact with the stepped portion a, and the nut 32 is pressed against the outer side surface of the inner race 27a2. 27 is tightened so as to be restricted from moving in the axial direction.

5 (a) and 5 (b) show the inner race 27a3 of the tapered roller bearing 27 that has been further modified. The inner race 27a3 is formed with a notch 80a on one end side (conical shape side) every 180 degrees. On the other hand, a stepped portion a is formed on the tip side portion of the other side shaft portion 22b of the input side friction wheel 22, and a protrusion 81 is formed on the stepped portion a toward the tip side every 180 degrees. The small diameter side portion h of the stepped portion a is in a loose fitting relationship with the inner peripheral surface of the inner race 27a3. A male screw e is formed at the tip of the shaft 22b.

As a result, the stepped small-diameter side portion h of the other side shaft portion 22b of the input side friction wheel 22 is fitted in the inner peripheral surface of the inner race 27a3 in a loose fit (clearance fit) state, and is inserted into the notch portion 80a. The protrusions 81 are coupled and are non-rotatably connected. The inner race 27a3 is sandwiched between the stepped portion a and the nut 32 is fastened to the male screw portion e so that the inner race 27a3 is integrally attached to the shaft portion 22b in the axial direction. In the above description, the notch 80a is directly formed in the inner race, but this may be formed in a sleeve press-fitted into the inner race. The relationship between the notch and the protrusion may be reversed, that is, the notch may be formed on the shaft portion and the protrusion may be formed on the inner race or the sleeve.

The engagement between the spline portion 60c of the sleeve 60 or the spline portion 70c of the inner race 27a2 and the spline portion c of the shaft portion 22b, and the engagement between the notch portion 80a and the protrusion 81 constitute the rotation stop of the inner race. . The rotation stopper is not limited to the above-described configuration, and may be another configuration such as a key and a key groove.

The gear transmission is a geared gear transmission using a gear, but a rotation transmission device by meshing other than a gear such as a chain and a sprocket may be interposed in part.

Further, the transmission path of the gear transmission is configured to pass through the continuously variable transmission. However, the present invention is not limited to this, and the rotation of the electric motor is transmitted to the diff ring gear 41 without passing through the continuously variable transmission. You may make it do. In this case, the intermediate gear 19 is rotatably supported by the input shaft 6, and the rotation of the intermediate gear is transmitted to the continuously variable transmission output shaft 24 directly or via an idler gear.

Further, the above description has been given along the embodiment in which the drive device is applied to the hybrid drive device. However, the present invention is not limited to this. For example, the gear transmission device is a reverse gear transmission device, or a part of the torque is separated. As a gear transmission device such as a gear transmission device that uses a planetary gear that is transmitted and combined with the continuously variable transmission output to expand the transmission range of the continuously variable transmission device or share part of its transmission torque, The invention is also applicable to drive devices other than hybrid drive devices.

The present invention is a drive device in which a friction transmission such as a cone ring type and a gear transmission are combined, and is used in a hybrid drive device mounted on an automobile.

DESCRIPTION OF SYMBOLS 1 (Hybrid) drive device 2 Electric motor 3 Friction type (cone ring type) continuously variable transmission 4 Electric motor output shaft 5 Differential device 6 Input shaft 7 Gear transmission device 9 First case member 10 Second case member 11 Case 12 Bulkhead 22 Input member (conical friction wheel)
22a One side shaft portion 22b The other side shaft portion 23 Output member (conical friction wheel)
23a One side shaft portion 23b The other side shaft portion 24 Continuously variable transmission output shaft 25

Ring

26, 29, 30 Radial (roller) bearings 27, 31 (Tapered roller) bearings 27a, 27a2, 27a3 Inner race 32 Nut 60 Sleeve

60a collar part

60b, 70b large

diameter spigot part

60c,

70c spline part

60d, 70d small diameter spigot part 80a notch part 81 protrusion a stepped part b large diameter support part c spline part d small diameter support part e male thread part A first 1 space B 2nd space

Claims

A first space in which the friction type continuously variable transmission is housed and filled with traction oil, and a second space in which a gear transmission composed of rotation transmission means by meshing is housed and filled with lubricating oil In the drive device in which the case is partitioned in an oil-tight manner by a partition wall,
The friction type continuously variable transmission includes an input member formed of a conical friction wheel, and a conical shape arranged parallel to the input member and having a large-diameter portion and a small-diameter portion reversed in the axial direction. A cone ring type continuously variable transmission that has an output member composed of a friction wheel and a ring that is sandwiched between inclined surfaces facing each other, and that moves the ring in the axial direction to continuously change speed. ,
One of the input member and the output member has a shaft portion on one side thereof rotatably supported by the case and a shaft portion on the other side in the thrust direction on the second space side of the partition wall. Supported through a bearing that supports the radial direction,
The bearing is attached to the partition wall, and the inner race is non-rotatably connected to the shaft portion on the other side via a rotation stopper.
A drive device characterized by that.
The one member is an input member, the shaft portion on one side of the input member is on the large diameter portion side of the friction wheel, and the shaft portion on the other side is on the small diameter portion side of the friction wheel. is there,
The drive device according to claim 1.
Press-fit a sleeve into the inner race,
The sleeve has a spline portion between a large-diameter spigot portion, a small-diameter spigot portion and the two spigot portions on the inner diameter side thereof,
The shaft portion on the other side is supported by loose fitting on the both spigot portions and is spline-engaged with the spline portion.
The driving device according to claim 1 or 2.
The inner race has a spline portion between a large-diameter spigot portion, a small-diameter spigot portion and both the spigot portions on the inner diameter side thereof,
The shaft portion on the other side is supported by loose fitting on the both spigot portions and is spline-engaged with the spline portion.
The driving device according to claim 1 or 2.
While providing a stepped portion on the other side shaft portion, the stepped portion is provided with a protrusion or a notch,
A notch or protrusion is provided on one end face of the inner race, and the other side shaft is supported by the inner race by loose fitting, and the notch is engaged with the protrusion. Connected to be non-rotatable,
The driving device according to claim 1 or 2.
The shaft portion on the other side has a stepped portion and a male screw portion at the tip portion,
The inner race is tightened with a nut screwed to the male screw portion between the stepped portion, and the inner race is integrally attached to the shaft portion on the other side in the axial direction.
The drive device according to claim 1.
The bearing is a tapered roller bearing that supports a thrust force toward the large diameter portion of the input member.
The drive device according to claim 1.
The case has a first case member and a second case member coupled to each other,
The input member is supported by the first case member through a radial bearing at the one side shaft portion;
The output member is supported by the first case member through a radial bearing on one side shaft and supported by the partition wall through the radial bearing on the other side.
An axial force applying means for applying an axial force corresponding to an output torque is interposed between the output member and the continuously variable transmission output shaft;
The continuously variable transmission output shaft is supported on the second space side of the second case member via a tapered roller bearing that supports a thrust force in the reaction force direction of the axial force applying means. ,
The drive device according to any one of claims 1 to 7.
An input shaft linked to the engine,
An electric motor having a dedicated output shaft;
A differential device,
The friction type continuously variable transmission continuously changes the rotation of the input shaft and outputs it to the continuously variable transmission output shaft;
The gear transmission is configured to transmit the rotation of the output shaft of the electric motor to the differential device via the continuously variable transmission output shaft.
The drive device according to claim 8.